EP3141728B1 - Moteur à combustion interne - Google Patents

Moteur à combustion interne Download PDF

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Publication number
EP3141728B1
EP3141728B1 EP16187408.6A EP16187408A EP3141728B1 EP 3141728 B1 EP3141728 B1 EP 3141728B1 EP 16187408 A EP16187408 A EP 16187408A EP 3141728 B1 EP3141728 B1 EP 3141728B1
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EP
European Patent Office
Prior art keywords
intake
angle
intake port
recess
combustion chamber
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP16187408.6A
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German (de)
English (en)
Other versions
EP3141728A1 (fr
Inventor
Yasuhiro Yamamoto
Taketo Nagasaki
Yosuke Miyamoto
Naoyuki Miyara
Hajime Takagawa
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Toyota Motor Corp
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Toyota Motor Corp
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Publication date
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Publication of EP3141728A1 publication Critical patent/EP3141728A1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F1/00—Cylinders; Cylinder heads 
    • F02F1/24—Cylinder heads
    • F02F1/42—Shape or arrangement of intake or exhaust channels in cylinder heads
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B23/00—Other engines characterised by special shape or construction of combustion chambers to improve operation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B31/00—Modifying induction systems for imparting a rotation to the charge in the cylinder
    • F02B31/04—Modifying induction systems for imparting a rotation to the charge in the cylinder by means within the induction channel, e.g. deflectors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F1/00—Cylinders; Cylinder heads 
    • F02F1/24—Cylinder heads
    • F02F1/42—Shape or arrangement of intake or exhaust channels in cylinder heads
    • F02F1/4235—Shape or arrangement of intake or exhaust channels in cylinder heads of intake channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F1/00—Cylinders; Cylinder heads 
    • F02F1/24—Cylinder heads
    • F02F1/42—Shape or arrangement of intake or exhaust channels in cylinder heads
    • F02F1/4285—Shape or arrangement of intake or exhaust channels in cylinder heads of both intake and exhaust channel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B2275/00—Other engines, components or details, not provided for in other groups of this subclass
    • F02B2275/48—Tumble motion in gas movement in cylinder
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the invention relates to an internal combustion engine that introduces the intake air into a combustion chamber through an intake port, thereby generating a tumble flow in the combustion chamber.
  • JP 2008-255860 A discloses an internal combustion engine that generates a tumble flow in a combustion chamber. That is, as shown in FIG. 11 , the intake air introduced into a combustion chamber 510 through an intake port 500 flows in a counterclockwise direction in the figure, thereby generating a tumble flow in the combustion chamber 510.
  • a cylinder head 520 of this internal combustion engine is provided with a tubular valve guide 540 by which a stem 531 of an intake valve 530 is slidably supported.
  • One end in a longitudinal direction of the valve guide 540 i.e. lower end of the valve guide 540 in FIG. 11 ) protrudes into the intake port 500.
  • a groove 502 is provided which extends in an extending direction of the intake port 500 around the valve guide 540. That is, the groove 502 is provided on the peripheral surface 501 of the intake port 500 at a portion on the side away from the combustion chamber 510 (i.e. on the upper side of the peripheral surface 501 in FIG. 11 ). With this configuration, a portion of the intake air flowing in the intake port 500 flows in the groove 502 so that the flow of the intake air that bypasses the valve guide 540 can be formed in the intake port 500.
  • JP2009007953 and US5423300 disclose engines with an enlarged portion, on both sides in an extending direction of the output shaft, in the connecting portion of the intake port.
  • the depth of the groove 502 gradually decreases as approaching its downstream end. Then, as shown by a broken-line arrow in FIG. 11 , the intake air that flows in the groove 502 and flows out of its downstream end will flow toward an umbrella part 532 of the intake valve 530 when the intake valve 530 opens. That is, in the intake port 500, while the flow of the intake air that bypasses the valve guide 540 can be produced by providing the groove 502, the flow of the intake air directed vertical downwardly into the combustion chamber 510 is also produced.
  • the vertical downward flow of the intake air is a branch flow
  • the flow of the intake air that flows into the combustion chamber 510 from the intake port 500 without flowing into the groove 502 is a main flow
  • the main flow is pushed by the branch flow toward the piston 550 side, i.e. downward direction in the figure. This may change the flow direction of the intake air forming the main flow.
  • the intake air flowing into the combustion chamber 510 from the intake port 500 is less likely to proceed to an umbrella part 561 of an exhaust valve 560 so that, as shown by a solid-line arrow in FIG. 11 , the turning radius of the flow of the intake air decreases. Therefore, a strong tumble flow may be difficult to occur in the combustion chamber 510.
  • an internal combustion engine is configured to introduce intake air to a combustion chamber and generate a tumble flow in the combustion chamber
  • the internal combustion engine includes a cylinder head, an intake valve including an umbrella part, and an output shaft.
  • the cylinder head includes an intake port.
  • the intake port is connected to the combustion chamber.
  • the intake port includes a connecting portion and an upstream portion, the connecting portion has a passage cross-sectional area that increases as approaching the combustion chamber, and the upstream portion is connected to an upstream end of the connecting portion.
  • the intake port includes a valve seat provided at a downstream end of the connecting portion, and the umbrella part of the intake valve is configured to contact with the valve seat.
  • the intake port has a recess provided at at least one of portions, on both sides in an extending direction of the output shaft, of a peripheral surface of the intake port, the recess spanning the connecting portion and the upstream portion.
  • the recess is provided at at least one of the portions, on both sides in the extending direction of the engine output shaft, of the peripheral surface of the intake port.
  • the recess is opened at the peripheral surface of the connecting portion of the intake port. A portion of the intake air flowing in the intake port flows into the recess and then flows into the combustion chamber from a downstream end of the recess. Therefore, the intake air flowing out of the downstream end of the recess is suppressed to flow perpendicularly into the combustion chamber.
  • the flow of the intake air flowing into the combustion chamber through the intake port without flowing into the recess is a main flow
  • the flow of the intake air flowing into the combustion chamber after flowing in the recess is a branch flow
  • the main flow is unlikely to be pushed to the piston side by the branch flow.
  • the intake air flowing into the combustion chamber from the intake port flows along a combustion chamber wall surface. That is, the turning radius of the flow of the intake air in the combustion chamber is unlikely to be small. Therefore, it is possible to suppress a reduction in the turning radius of the flow of the intake air in the combustion chamber.
  • a strong tumble flow is generated in the combustion chamber.
  • the recess extends substantially in an extending direction of the intake port and is configured such that the flow of the intake air flows into the combustion chamber from the intake port without flowing into the recess in a main flow while the flow of the intake air flows into the combustion chamber after flowing in the recess in a branch flow.
  • a downstream end of the recess is located upstream of the valve seat in the connecting portion.
  • a depth of the recess with respect to the peripheral surface of the upstream portion gradually increases as going downstream from its upstream end.
  • the intake connecting portion has a portion on the side away from the exhaust valve which is connected at a substantially right angle to the intake upstream portion.
  • the internal combustion engine may further include a cylinder block and an exhaust valve including an umbrella part.
  • the cylinder head may be mounted on the cylinder block.
  • the cylinder head includes a mounting surface, and the mounting surface may be a surface mounted on the cylinder block.
  • the umbrella part of the exhaust valve may include an exhaust valve bottom surface.
  • the exhaust valve bottom surface may be a surface facing the combustion chamber.
  • the umbrella part of the intake valve may include a port-side umbrella surface.
  • the port-side umbrella surface may be a surface facing the intake port.
  • a value obtained by dividing a sum of a recess angle and an intake-side inclination angle by 2 may be greater than zero and less than or equal to an exhaust bottom surface angle, where the recess angle is an angle of an extending direction of the recess with respect to the mounting surface, the intake-side inclination angle is an inclination angle of a portion, closest to the exhaust valve, of the port-side umbrella surface with respect to the mounting surface, and the exhaust bottom surface angle is an inclination angle of the exhaust valve bottom surface with respect to the mounting surface.
  • the intake air (main flow and branch flow) flowing into the combustion chamber from the intake port flows toward the umbrella part of the exhaust valve and a flow direction of the intake air is changed by the exhaust valve bottom surface of the umbrella part. Thereafter, the intake air flows along the exhaust valve bottom surface and then flows along an inner peripheral surface of a cylinder toward a top surface of the piston.
  • the value obtained by dividing the sum of the recess angle and the intake-side inclination angle by "2" is a representative value of an angle of a flow direction of a branch flow with respect to the mounting surface. Therefore, it is difficult to cause the branch flow to flow along the exhaust valve bottom surface when the value is greater than the exhaust bottom surface angle.
  • an internal combustion engine 11 of this embodiment includes a cylinder block 12 and a cylinder head 13 mounted on an upper portion in the figure of the cylinder block 12.
  • a cylinder head 13 mounted on an upper portion in the figure of the cylinder block 12.
  • its lower surface in the figure mounted on the cylinder block 12 will be referred to as a "mounting surface 13A”.
  • the internal combustion engine 11 includes a plurality of cylinders 14 and a piston 15 that reciprocates vertically in the figure is provided in each cylinder 14.
  • An engine output shaft 16 extending in a direction perpendicular to the sheet surface.
  • the engine output shaft 16 is connected to the pistons 15 via connecting rods 17.
  • a combustion chamber 18 is formed between a top surface 151 of the piston 15 and the cylinder head 13.
  • a mixture of fuel and intake air is burned in the combustion chamber 18.
  • a surface defining the combustion chamber 18 will be referred to as a "combustion chamber wall surface 181.”
  • the combustion chamber wall surface 181 is constituted by an inner peripheral surface of the cylinder 14, the top surface 151 of the piston 15, and so on.
  • the cylinder head 13 is provided with intake ports 19 for introducing the intake air into the combustion chambers 18 and exhaust ports 20 for discharging the exhaust gas generated by the combustion of the mixture in the combustion chambers 18.
  • intake ports 19 for introducing the intake air into the combustion chambers 18
  • exhaust ports 20 for discharging the exhaust gas generated by the combustion of the mixture in the combustion chambers 18.
  • two intake ports 19 and two exhaust ports 20 are provided for each cylinder 14.
  • the intake air flows along the combustion chamber wall surface 181 so that a tumble flow is generated as shown by an arrow in FIG. 1 .
  • the internal combustion engine 11 further includes intake valves 30 each for opening and closing the intake port 19 with respect to the combustion chamber 18 and exhaust valves 40 each for opening and closing the exhaust port 20 with respect to the combustion chamber 18.
  • the valves 30 and 40 each have a rod-like stem 31, 41 and an umbrella part 32, 42 provided at a tip of the stem 31, 41.
  • the umbrella part 32 of the intake valve 30 has a port-side umbrella surface 321 as a surface facing the intake port 19 and an intake valve bottom surface 322 as a surface facing the combustion chamber 18.
  • the umbrella part 42 of the exhaust valve 40 has an exhaust valve bottom surface 421 as a surface facing the combustion chamber 18.
  • the intake valve bottom surface 322 and the exhaust valve bottom surface 421 each form a part of the surface forming the combustion chamber wall surface 181.
  • the valves 30 and 40 are each supported by a generally circular tubular valve guide 21, 22 so as to be movable in an axial direction of the stem 31, 41 with respect to the cylinder head 13.
  • the intake port 19 has an intake connecting portion 191 as a connecting portion to the combustion chamber 18 and an intake upstream portion 192 as an upstream portion connected to an upstream end of the intake connecting portion 191.
  • An intake valve seat 26 with which the umbrella part 32 of the intake valve 30 is brought into contact is provided at a downstream end of the intake connecting portion 191.
  • the intake valve seat 26 is a laser-clad valve seat.
  • the exhaust port 20 has an exhaust connecting portion 201 as a connecting portion to the combustion chamber 18 and the exhaust connecting portion 201 is provided with an exhaust valve seat 27 with which the umbrella part 42 of the exhaust valve 40 is brought into contact.
  • the intake connecting portion 191 has a passage cross-sectional area that increases as approaching the combustion chamber 18.
  • its portion on the side away from the exhaust valve 40 i.e. on the obliquely right lower side in the figure
  • the intake connecting portion 191 will be referred to as a "separation wall 191A".
  • an extending direction of the engine output shaft 16 i.e. a vertical direction in FIG. 2
  • recesses 50 each extending in an extending direction of the intake port 19 are provided at respective portions, on both sides in the predetermined direction, of a peripheral surface 19A of the intake port 19. Downstream ends of the recesses 50 are located upstream of the valve seat 26 in the intake connecting portion 191, while each recess 50 spans the intake upstream portion 192 and the intake connecting portion 191.
  • the depth of the recess 50 gradually increases as going downstream from its upstream end. That is, the recess 50 is configured to be deepest at its downstream end.
  • FIG. 3 shows a part of an unfinished cylinder head material 130, which is the cylinder head 13 during processing.
  • the cylinder head 13 is formed by processing the unfinished cylinder head material 130.
  • in the unfinished cylinder head material 130 at a portion that will be the intake connecting portion 191 of the intake port 19, there are provided an annular clad deposition groove 131 and an annular bottom plate portion 132 projecting radially inward and located at a position farther from the combustion chamber 18 than the clad deposition groove 131.
  • a processing part 210 located at its lower end in the figure has a two-step tapered shape. That is, the diameter of a first tapered portion 211 of the processing part 210 and the diameter of a second tapered portion 212 located on the side forward of the first tapered portion 211 each decrease as going downward in the figure.
  • the decreasing gradient of the diameter of the second tapered portion 212 is smaller than the decreasing gradient of the diameter of the first tapered portion 211.
  • the bottom plate removal cutter 200 By moving the bottom plate removal cutter 200 downward while rotating it, the bottom plate portion 132 is cut. In this event, a portion, near the exhaust port 20, of the bottom plate portion 132 is mostly cut off. In addition to the bottom plate portion 132, the body of the unfinished cylinder head material 130 is also cut off slightly by the bottom plate removal cutter 200. With this configuration, the passage cross-sectional area of the intake connecting portion 191 of the intake port 19 increases as approaching the combustion chamber 18 and further the intake connecting portion 191 is provided with the separation wall 191A.
  • the shape of an inner peripheral surface of the copper alloy described above is also processed by the bottom plate removal cutter 200.
  • the intake valve seat 26 is formed at the downstream end of the intake connecting portion 191 of the intake port 19.
  • the recess processing cutter 300 has a generally cylindrical shape. By moving the recess processing cutter 300 into the intake port 19 while rotating it, a part of the peripheral surface 19A of the intake port 19 is cut off. As a result, the recess 50 extending in the extending direction of the intake port 19 is formed in the intake port 19.
  • FIGS. 6 and 7 the degree of the inclination of the recess 50 will be described.
  • Various angles shown in FIG. 6 are relative angles with respect to the mounting surface 13A of the cylinder head 13.
  • An inclination angle of the exhaust valve bottom surface 421 of the umbrella part 42 of the exhaust valve 40 with respect to the mounting surface 13A is given as an "exhaust bottom surface angle ⁇ (e.g. 15 to 35°)"
  • an inclination angle of a portion, closest to the exhaust valve 40, of the port-side umbrella surface 321 of the umbrella part 32 of the intake valve 30 with respect to the mounting surface 13A is given as an "intake-side inclination angle ⁇ (e.g. -20 to +15°)”
  • an inclination angle of an extending direction of the recess 50 with respect to the mounting surface 13A is given as a "recess angle ⁇ (e.g. 20 to 55°)”.
  • the first middle line angle ⁇ is greater than "0 (zero)” and less than or equal to the exhaust bottom surface angle ⁇ .
  • the recess 50 is formed so as to satisfy the following relational expression (1). ⁇ ⁇ ⁇ ⁇ 2 ⁇ ⁇ ⁇ That is, the upper limit of the recess angle ⁇ is an angle equal to "2 ⁇ ⁇ - ⁇ ".
  • the recess 50 of which the recess angle ⁇ is "- ⁇ " is unable to be formed on the peripheral surface 19A of the intake port 19. Therefore, the lower limit of the recess angle ⁇ may be considered to be "0 (zero)".
  • the recess 50 is formed by moving the recess processing cutter 300 into the intake port 19 from the combustion chamber 18 side. Therefore, when the recess angle ⁇ is "0 (zero)", it is not possible to advance the recess processing cutter 300 into the intake port 19.
  • the actual lower limit of the recess angle ⁇ is greater than "0 (zero)" and is defined by the shape such as the diameter of the recess processing cutter 300.
  • the recess 50 is configured to extend in the extending direction of the intake port 19. Therefore, an inclination angle of the extending direction of the intake port 19 with respect to the mounting surface 13A has some correlation with the recess angle ⁇ .
  • the umbrella part 32 of the intake valve 30 includes, in addition to the port-side umbrella surface 321 and the intake valve bottom surface 322, a first connecting surface 323 and a second connecting surface 324.
  • the first connecting surface 323 is a surface connecting between a peripheral surface of the stem 31 of the intake valve 30 and the port-side umbrella surface 321.
  • the second connecting surface 324 is a surface connecting between the port-side umbrella surface 321 and the intake valve bottom surface 322.
  • the first connecting surface 323 is connected to a radially inward end of the port-side umbrella surface 321, while the second connecting surface 324 is connected to a radially outward end of the port-side umbrella surface 321.
  • the first connecting surface 323 has a circular arc shape.
  • the port-side umbrella surface 321 and the second connecting surface 324 each have a substantially straight shape, the radial length of the second connecting surface 324 is extremely short compared to the radial length of the port-side umbrella surface 321.
  • FIGS. 8 and 9 the degree of the inclination of the intake connecting portion 191 of the intake port 19 will be described.
  • Various angles shown in FIG. 8 are relative angles with respect to the mounting surface 13A of the cylinder head 13.
  • a portion extending in the extending direction of the intake port 19 from a position closest to the exhaust valve seat 27 in the peripheral surface 19A of the intake port 19 is given as an "intake port upper wall surface 19A1" and an inclination angle of the intake port upper wall surface 19A1 with respect to the mounting surface 13A is given as an “intake port upper wall surface angle ⁇ (e.g. 30 to 45°)".
  • the second middle line angle ⁇ is less than or equal to the exhaust bottom surface angle ⁇ . That is, ( ⁇ + ⁇ ) / 2 ⁇ ⁇ .
  • the intake connecting portion 191 is formed so as to satisfy the following relational expression (2). ⁇ ⁇ 2 ⁇ ⁇ ⁇ ⁇
  • the intake port upper wall surface angle ⁇ can be obtained as explained below. That is, as shown in FIG.
  • an intersection point A1 between the intake port upper wall surface 19A1 and a perpendicular line L1 passing through a portion A between the separation wall 191 A of the intake connecting portion 191 and the intake upstream portion 192 in the intake port 19 and being perpendicular to the intake port upper wall surface 19A1, and a downstream end A2 of the intake connecting portion 191 in the intake port upper wall surface 19A1 are set.
  • an inclination angle of a straight line L2 connecting between the intersection point A1 and the downstream end A2 with respect to the mounting surface 13A is given as the intake port upper wall surface angle ⁇ .
  • an angle of a flow direction of the main flow X1 with respect to the mounting surface 13A is determined by the intake port upper wall surface angle ⁇ being the inclination angle of the intake port upper wall surface 19A1 of the intake port 19 and the intake-side inclination angle ⁇ . Therefore, the angle of the flow direction of the main flow X1 with respect to the mounting surface 13A can be presumed to be smaller than the intake port upper wall surface angle ⁇ and greater than the intake-side inclination angle ⁇ .
  • the second middle line angle ⁇ being the value obtained by dividing the sum of the intake port upper wall surface angle ⁇ and the intake-side inclination angle ⁇ by "2" is set to be greater than "0 (zero)" and less than or equal to the exhaust bottom surface angle ⁇ being the inclination angle of the exhaust valve bottom surface 421.
  • the second middle line angle ⁇ is the representative value of the angle of the flow direction of the main flow X1 with respect to the mounting surface 13A. Therefore, the main flow X1 flowing into the combustion chamber 18 from the intake port 19 collides with the exhaust valve bottom surface 421 and, thereafter, the intake air forming the main flow X1 flows along the exhaust valve bottom surface 421.
  • the second middle line angle ⁇ is greater than the exhaust bottom surface angle ⁇ .
  • the inclination angle, with respect to the mounting surface 13A, of the flow direction of the main flow X1 flowing into the combustion chamber 18 from the intake port 19 tends to be greater than the exhaust bottom surface angle ⁇ . Therefore, it is difficult to cause the intake air to flow along the exhaust valve bottom surface 421 so that the turning radius of the flow of the intake air flowing into the combustion chamber 18 from the intake port 19 tends to be small.
  • an angle, with respect to the mounting surface 13A, of a flow direction of the branch flow X2 being the flow of the intake air flowing into the combustion chamber 18 after flowing in the recess 50 is determined by the recess angle ⁇ and the intake-side inclination angle ⁇ . Therefore, the angle of the flow direction of the branch flow X2 with respect to the mounting surface 13A can be presumed to be smaller than the recess angle ⁇ and greater than the intake-side inclination angle ⁇ .
  • the first middle line angle ⁇ being the value obtained by dividing the sum of the recess angle ⁇ and the intake-side inclination angle ⁇ by "2" is set to be greater than "0 (zero)" and less than or equal to the exhaust bottom surface angle ⁇ being the inclination angle of the exhaust valve bottom surface 421.
  • the first middle line angle ⁇ is the representative value of the angle of the flow direction of the branch flow X2 with respect to the mounting surface 13A. Therefore, the branch flow X2 having passed through the recess 50 also flows along the exhaust valve bottom surface 421.
  • the first middle line angle ⁇ is greater than the exhaust bottom surface angle ⁇ .
  • the inclination angle, with respect to the mounting surface 13A, of the flow direction of the branch flow X2 being the flow of the intake air flowing into the combustion chamber 18 after flowing in the recess 50 tends to be greater than the exhaust bottom surface angle ⁇ . Therefore, it is difficult to cause the intake air forming the branch flow X2 to flow along the exhaust valve bottom surface 421 so that the turning radius of the flow of a portion of the intake air (i.e. the intake air forming the branch flow X2) flowing into the combustion chamber 18 from the intake port 19 tends to be small.
  • the recesses 50 are provided at respective portions, on both sides in the predetermined direction, of the peripheral surface 19A of the intake port 19 and each extend in the extending direction of the intake port 19. Therefore, the branch flows X2 flowing out of the recesses 50 of the intake port 19 do not flow substantially perpendicularly (downward in FIG. 1 ) toward the inside of the combustion chamber 18. Accordingly, the main flow X1 flowing into the combustion chamber 18 from the intake port 19 without flowing into the recess 50 is unlikely to be pushed to the piston 15 side (i.e. the lower side in FIG. 1 ) by the branch flows X2.
  • the recess 50 is configured to be deepest at its downstream end. Therefore, as shown in FIG. 10 , the branch flows X2 flow along the main flow X1 on both sides in the predetermined direction of the main flow X1. As a result, it is suppressed that the main flow X1 and the branch flows X2 collide with each other in the intake port 19 immediately before flowing into the combustion chamber 18, and therefore, the occurrence of turbulence in the vicinity of the umbrella part 32 of the intake valve 30 is suppressed.
  • the intake air flowing into the combustion chamber 18 from the intake port 19 proceeds to the exhaust valve bottom surface 421 of the umbrella part 42 of the exhaust valve 40. Then, the intake air whose flow direction is changed by the exhaust valve bottom surface 421 flows along the exhaust valve bottom surface 421 and then flows along the inner peripheral surface of the cylinder 14 toward the piston 15. Thereafter, the intake air having reached the top surface 151 of the piston 15 flows along the top surface 151 and then flows along the inner peripheral surface of the cylinder 14 toward the intake valve 30. In this event, when the intake valve 30 is not yet closed, the intake air flowing in the combustion chamber 18 in this way joins the intake air flowing in from the intake port 19 and flows in the combustion chamber 18 along the combustion chamber wall surface 181 in a counterclockwise direction in FIG. 1 .
  • the recesses 50 are provided at respective portions, on both sides in the predetermined direction, of the peripheral surface 19A of the intake port 19.
  • the recess 50 may be provided only at either one of the portions, on both sides in the predetermined direction, of the peripheral surface 19A of the intake port 19. That is, the recess 50 may be provided only at the outer portion or at the inner portion, in the predetermined direction, of the portions, on both sides in the predetermined direction, of the peripheral surface 19A of the intake port 19. Even in this case, compared to a case in which no recess 50 is provided on the peripheral surface 19A of the intake port 19, it is possible to increase the flow amount of the intake air from the intake port 19 into the combustion chamber 18.
  • the number of the intake ports 19 provided for each cylinder 14 may be a number other than two (e.g. one or three). Even in this case, by providing the recess 50 at at least one of the portions, on both sides in the predetermined direction, of the peripheral surface 19A of the intake port 19, the effects similar to (1) and (2) described above can be obtained.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
  • Combustion Methods Of Internal-Combustion Engines (AREA)

Claims (9)

  1. Moteur à combustion interne (11) qui est configuré pour introduire de l'air d'admission dans une chambre de combustion (18) et générer un flux de tourbillonnement dans la chambre de combustion (18), le moteur à combustion interne (11) comprenant :
    une culasse (13) ;
    une soupape d'admission (30) incluant une partie d'ombrelle (32) ; et
    un arbre de sortie (16),
    dans lequel
    la culasse (13) inclut un orifice d'admission (19),
    l'orifice d'admission (19) est raccordé à la chambre de combustion (18),
    l'orifice d'admission (19) inclut une portion de raccordement (191) et une portion en amont (192), la portion de raccordement (191) a une aire en coupe transversale de passage qui augmente à l'approche de la chambre de combustion (18), et la portion en amont (192) est raccordée à une extrémité en amont de la portion de raccordement (191),
    l'orifice d'admission (19) inclut un siège de soupape (26) prévu au niveau d'une extrémité en aval de la portion de raccordement (191), et la partie d'ombrelle (32) de la soupape d'admission (30) est configurée pour venir en contact avec le siège de soupape (26),
    l'orifice d'admission (19) a un évidement (50) prévu au niveau d'au moins l'une de portions, des deux côtés dans un sens d'extension de l'arbre de sortie (16), d'une surface périphérique (19A) de l'orifice d'admission (19), l'évidement (50) chevauchant la portion de raccordement (191) et la portion en amont (192),
    caractérisé en ce que
    l'évidement (50) est formé par la découpe d'une partie de la surface périphérique (19A) de l'orifice d'admission (19).
  2. Moteur à combustion interne (11) selon la revendication 1, dans lequel une extrémité en aval de l'évidement (50) est située en amont du siège de soupape (26) dans la portion de raccordement (191).
  3. Moteur à combustion interne (11) selon la revendication 1 ou 2, dans lequel une profondeur de l'évidement (50) par rapport à la surface périphérique de la portion en amont (192) augmente progressivement en allant en aval depuis son extrémité en amont.
  4. Moteur à combustion interne (11) selon l'une quelconque des revendications 1 à 3, dans lequel
    le moteur à combustion interne comprend en outre une soupape d'échappement (40), et
    la portion de raccordement d'admission (191) a une portion (191A) sur le côté éloigné de la soupape d'échappement (40) qui est raccordée à un angle sensiblement droit à la portion en amont d'admission (192).
  5. Moteur à combustion interne (11) selon l'une quelconque des revendications 1 à 4, comprenant en outre
    un bloc-cylindres (12), et
    une soupape d'échappement (40) incluant une partie d'ombrelle,
    dans lequel
    la culasse (13) est montée sur le bloc-cylindres (12),
    la culasse (13) inclut une surface de montage, la surface de montage est une surface montée sur le bloc-cylindres (12),
    la partie d'ombrelle de la soupape d'échappement (40) inclut une surface de fond de soupape d'échappement, la surface de fond de soupape d'échappement est une surface faisant face à la chambre de combustion (18),
    la partie d'ombrelle (32) de la soupape d'admission (30) inclut une surface d'ombrelle côté orifice, la surface d'ombrelle côté orifice est une surface faisant face à l'orifice d'admission (19), et
    une valeur (ρ) obtenue en divisant une somme d'un angle d'évidement (ε) et d'un angle d'inclinaison côté admission (β) par 2 est supérieure à zéro et inférieure ou égale à un angle de surface de fond d'échappement (θ), où l'angle d'évidement (ε) est un angle d'un sens d'extension de l'évidement (50) par rapport à la surface de montage, l'angle d'inclinaison côté admission (β) est un angle d'inclinaison d'une portion, la plus proche de la soupape d'échappement (40), de la surface d'ombrelle côté orifice par rapport à la surface de montage, et l'angle de surface de fond d'échappement (θ) est un angle d'inclinaison de la surface de fond de soupape d'échappement par rapport à la surface de montage.
  6. Moteur à combustion interne (11) selon la revendication 5, dans lequel la portion de raccordement (191) a une surface de paroi supérieure d'orifice d'admission (191A) s'étendant depuis une position la plus proche d'un siège de soupape d'échappement (27) de la soupape d'échappement (40) dans la surface périphérique (19A) de l'orifice d'admission (19), et
    une valeur (γ) obtenue en divisant une somme d'un angle de surface de paroi supérieure d'orifice d'admission (α) et de l'angle d'inclinaison côté admission (β) par 2 est supérieure à zéro et inférieure ou égale à l'angle de surface de fond d'échappement (θ), où l'angle de surface de paroi supérieure d'orifice d'admission (α) est un angle d'un sens d'extension de la surface de paroi supérieure d'orifice d'admission (191A) par rapport à la surface de montage.
  7. Moteur à combustion interne (11) selon la revendication 6, dans lequel une valeur absolue d'une différence entre l'angle de surface de paroi supérieure d'orifice d'admission (α) et l'angle d'évidement (ε) est inférieure ou égale à 10°.
  8. Moteur à combustion interne (11) selon la revendication 7, dans lequel l'angle de surface de paroi supérieure d'orifice d'admission (α) est supérieur à l'angle d'évidement (ε).
  9. Moteur à combustion interne (11) selon l'une quelconque des revendications précédentes, dans lequel l'évidement (50) est prévu au niveau de chacune de portions respectives, des deux côtés dans le sens d'extension de l'arbre de sortie (16), de la surface périphérique (19A) de l'orifice d'admission (19).
EP16187408.6A 2015-09-08 2016-09-06 Moteur à combustion interne Active EP3141728B1 (fr)

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JP2015176934A JP6288014B2 (ja) 2015-09-08 2015-09-08 内燃機関

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CN106499541B (zh) 2019-08-13
EP3141728A1 (fr) 2017-03-15
CN106499541A (zh) 2017-03-15
JP2017053259A (ja) 2017-03-16
US20170067390A1 (en) 2017-03-09
US10233825B2 (en) 2019-03-19
JP6288014B2 (ja) 2018-03-07

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